Multi-speed transmission having three planetary gear sets

ABSTRACT

A transmission is provided having an input member, an output member, three planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices include clutches and brakes.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority to U.S. Provisional Application No.61/231,591, filed on Aug. 5, 2009, which is hereby incorporated in itsentirety herein by reference.

FIELD

The invention relates generally to a multiple speed transmission havinga plurality of planetary gear sets and a plurality of torquetransmitting devices and more particularly to a transmission having sixor more speeds, three planetary gear sets and a plurality of torquetransmitting devices.

BACKGROUND

The statements in this section merely provide background informationrelated to the present disclosure and may or may not constitute priorart.

A typical multiple speed transmission uses a combination of frictionclutches, planetary gear arrangements and fixed interconnections toachieve a plurality of gear ratios. The number and physical arrangementof the planetary gear sets, generally, are dictated by packaging, costand desired speed ratios.

While current transmissions achieve their intended purpose, the need fornew and improved transmission configurations which exhibit improvedperformance, especially from the standpoints of efficiency,responsiveness and smoothness and improved packaging, primarily reducedsize and weight, is essentially constant. Accordingly, there is a needfor an improved, cost-effective, compact multiple speed transmission.

SUMMARY

A transmission is provided having an input member, an output member,three planetary gear sets, a plurality of coupling members and aplurality of torque transmitting devices. Each of the planetary gearsets includes first, second and third members. The torque transmittingdevices are for example clutches and brakes.

In another embodiment of the present invention, the first, second andthird planetary gear sets each having a sun gear, a carrier member and aring gear.

In yet another embodiment of the present invention, the input member iscontinuously connected for common rotation with the sun gear of thesecond planetary gear set.

In yet another embodiment of the present invention, the output member iscontinuously connected for common rotation with the carrier member ofthe second planetary gear set and to ring gear of the third planetarygear set.

In yet another embodiment of the present invention, a firstinterconnecting member continuously interconnects the carrier member ofthe first planetary gear set with the ring gear of the second planetarygear set.

In yet another embodiment of the present invention, a secondinterconnecting member continuously interconnects the sun gear of thefirst planetary gear set with a stationary member.

In yet another embodiment of the present invention, a thirdinterconnecting member continuously interconnects the carrier member ofthe second planetary gear set with the ring gear of the third planetarygear set.

In still another embodiment of the present invention, a first torquetransmitting mechanism is selectively engageable to interconnect thering gear of the first planetary gear set with the carrier member of thethird planetary gear set.

In still another embodiment of the present invention, a second torquetransmitting mechanism is selectively engageable to interconnect the sungear of the second planetary gear set with the carrier member of thethird planetary gear set.

In still another embodiment of the present invention, a third torquetransmitting mechanism is selectively engageable to interconnect the sungear of the second planetary gear set with the sun gear of the thirdplanetary gear set.

In still another embodiment of the present invention, a fourth torquetransmitting mechanism is selectively engageable to interconnect the sungear of the third planetary gear set with the stationary member.

In still another embodiment of the present invention, a fifth torquetransmitting mechanism is selectively engageable to interconnect thecarrier member of the third planetary gear set with the stationarymember.

In still another embodiment of the present invention, the input memberis continuously connected for common rotation with the sun gear of thethird planetary gear set.

In still another embodiment of the present invention, an output memberis continuously connected for common rotation with the carrier member ofthe first planetary gear set and to ring gear of the second planetarygear set.

In yet another embodiment of the present invention, a first torquetransmitting mechanism is selectively engageable to interconnect the sungear of the second planetary gear set with the sun gear of the thirdplanetary gear set.

In yet another embodiment of the present invention, a second torquetransmitting mechanism is selectively engageable to interconnect thecarrier member of the second planetary gear set with the sun gear of thethird planetary gear set.

In yet another embodiment of the present invention, a third torquetransmitting mechanism is selectively engageable to interconnect thering gear of the first planetary gear set with the carrier member of thethird planetary gear set.

In yet another embodiment of the present invention, a fourth torquetransmitting mechanism is selectively engageable to interconnect the sungear of the second planetary gear set with the stationary member.

In yet another embodiment of the present invention, a fifth torquetransmitting mechanism is selectively engageable to interconnect thecarrier member of the second planetary gear set with the stationarymember.

In yet another embodiment of the present invention, the torquetransmitting mechanisms are selectively engageable in combinations of atleast two to establish at least six forward speed ratios and at leastone reverse speed ratio between the input member and the output member.

Further features, aspects and advantages of the present invention willbecome apparent by reference to the following description and appendeddrawings wherein like reference numbers refer to the same component,element or feature.

DRAWINGS

The drawings described herein are for illustration purposes only and arenot intended to limit the scope of the present disclosure in any way.

FIG. 1 is a lever diagram of an embodiment of a six speed transmissionaccording to the present invention;

FIG. 2 is a diagrammatic illustration of an embodiment of a six speedtransmission according to the present invention;

FIG. 3 is a truth table presenting the state of engagement of thevarious torque transmitting elements in each of the available forwardand reverse speeds or gear ratios of the transmission illustrated inFIGS. 1 and 2.

FIG. 4 is a lever diagram of another embodiment of a six speedtransmission according to the present invention;

FIG. 5 is a diagrammatic illustration of another embodiment of a sixspeed transmission according to the present invention; and

FIG. 6 is a truth table presenting the state of engagement of thevarious torque transmitting elements in each of the available forwardand reverse speeds or gear ratios of the transmission illustrated inFIGS. 4 and 5.

DETAILED DESCRIPTION

The following description is merely exemplary in nature and is notintended to limit the present disclosure, application, or uses.

At the outset, it should be appreciated that the embodiments of the sixspeed automatic transmission of the present invention have anarrangement of permanent mechanical connections between the elements ofthe three planetary gear sets. A second component or element of a firstplanetary gear set is permanently coupled to a third component orelement of the second planetary gear set. A third component or elementof the first planetary gear set is permanently coupled to a ground orstationary member. A second component or element of the second planetarygear set is permanently coupled to a third component or element of thethird planetary gear set.

Referring now to FIG. 1, an embodiment of a six speed transmission 10 isillustrated in a lever diagram format. A lever diagram is a schematicrepresentation of the components of a mechanical device such as anautomatic transmission. Each individual lever represents a planetarygear set wherein the three basic mechanical components of the planetarygear are each represented by a node. Therefore, a single lever containsthree nodes: one for the sun gear, one for the planet gear carrier, andone for the ring gear. In some cases, two levers may be combined into asingle lever having more than three nodes (typically four nodes). Forexample, if two nodes on two different levers are interconnected througha fixed connection they may be represented as a single node on a singlelever. The relative length between the nodes of each lever can be usedto represent the ring-to-sun ratio of each respective gear set. Theselever ratios, in turn, are used to vary the gear ratios of thetransmission in order to achieve an appropriate ratios and ratioprogression. Mechanical couplings or interconnections between the nodesof the various planetary gear sets are illustrated by thin, horizontallines and torque transmitting devices such as clutches and brakes arepresented as interleaved fingers. Further explanation of the format,purpose and use of lever diagrams can be found in SAE Paper 810102, “TheLever Analogy: A New Tool in Transmission Analysis” by Benford andLeising which is hereby fully incorporated by reference.

The transmission 10 includes an input shaft or member 12, a firstplanetary gear set 14, a second planetary gear set 16 and a thirdplanetary gear set 18 and an output shaft or member 22. In the leverdiagram of FIG. 1, the first planetary gear set 14 has three nodes: afirst node 14A, a second node 14B and a third node 14C. The secondplanetary gear set 16 has three nodes: a first node 16A, a second node16B and a third node 16C. The third planetary gear set 18 has threenodes: a first node 18A, a second node 18B and a third node 18C.

The input member 12 is continuously coupled to the first node 16A of thesecond planetary gear set 16. The output member 22 is coupled to thesecond node 16B of the second planetary gear set 16. The second node 14Bof the first planetary gear set 14 is coupled to the third node 16C ofthe second planetary gear set 16. The third node 14C of the firstplanetary gear set 14 is coupled to a stationary member or transmissionhousing 50. The second node 16B of the second planetary gear set 16 iscoupled to the third node 18C of the third planetary gear set 18.

A first clutch 26 selectively connects the first node 14A of the firstplanetary gear set 14 with the second node 18B of the third planetarygear set 18. A second clutch 28 selectively connects the first node 16Aof the second planetary gear set 16 and the input member or shaft 12with the second node 18B of the third planetary gear set 18. A thirdclutch 30 selectively connects the first node 16A of the secondplanetary gear set 16 and the input member or shaft 12 with the firstnode 18A of the third planetary gear set 18. A first brake 32selectively connects the first node 18A of the third planetary gear set18 with a stationary member or transmission housing 50. A second brake34 selectively connects the second node 18B of the third planetary gearset 18 with a stationary member or transmission housing 50.

Referring now to FIG. 2, a stick diagram presents a schematic layout ofthe embodiment of the six speed transmission 10 according to the presentinvention. In FIG. 2, the numbering from the lever diagram of FIG. 1 iscarried over. The clutches and couplings are correspondingly presentedwhereas the nodes of the planetary gear sets now appear as components ofplanetary gear sets such as sun gears, ring gears, planet gears andplanet gear carriers.

For example, the planetary gear set 14 includes a sun gear member 14C, aring gear member 14A and a planet gear carrier member 14B that rotatablysupports a set of planet gears 14D (only one of which is shown). The sungear member 14C is connected to a stationary member or transmissionhousing 50 through a first shaft or interconnecting member 42. The ringgear member 14A is connected for common rotation with a second shaft orinterconnecting member 44. The planet carrier member 14B is connectedfor common rotation with and a third shaft or interconnecting member 46.The planet gears 14D are each configured to intermesh with both the sungear member 14C and the ring gear member 14A.

The planetary gear set 16 includes a sun gear member 16A, a ring gearmember 16C and a planet gear carrier member 16B that rotatably supportsa set of planet gears 16D (only one of which is shown). The sun gearmember 16A is connected for common rotation with a fourth shaft orinterconnecting member 48 and the input shaft or member 12. The ringgear member 16C is connected for common rotation with the third shaft orinterconnecting member 46. The planet carrier member 16B is connectedfor common rotation with a fifth shaft or interconnecting member 52 andwith the output shaft or member 22. The planet gears 16D are eachconfigured to intermesh with both the sun gear member 16A and the ringgear member 16C.

The planetary gear set 18 includes a sun gear member 18A, a ring gearmember 18C and a planet gear carrier member 18B that rotatably supportsa set of planet gears 18D (only one of which is shown). The sun gearmember 18A is connected for common rotation with a sixth shaft orinterconnecting member 54 and a seventh shaft or interconnecting member56. The ring gear member 18C is connected for common rotation with thefifth shaft or interconnecting member 52. The planet carrier member 18Bis connected for common rotation with an eighth shaft or interconnectingmember 58 and a ninth shaft or interconnecting member 60. The planetgears 18D are each configured to intermesh with both the sun gear member18A and the ring gear member 18C.

The input shaft or member 12 is continuously connected to an engine (notshown) or to a turbine of a torque converter (not shown). The outputshaft or member 22 is continuously connected with the final drive unitor transfer case (not shown).

The torque-transmitting mechanisms or clutches 26, 28, 30 and firstbrake 32 and second brake 34 allow for selective interconnection of theshafts or interconnecting members, members of the planetary gear setsand the housing. For example, the first clutch 26 is selectivelyengageable to connect the second shaft or interconnecting member 44 withthe ninth shaft or interconnecting member 60. The second clutch 28 isselectively engageable to connect the fourth shaft or interconnectingmember 48 with the eighth shaft or interconnecting member 58. The thirdclutch 30 is selectively engageable to connect the fourth shaft orinterconnecting member 48 with the seventh shaft or interconnectingmember 56. The first brake 32 is selectively engageable to connect thesixth shaft or interconnecting member 54 with the stationary element orthe transmission housing 50 in order to restrict the member 54 fromrotating relative to the transmission housing 50. The second brake 34 isselectively engageable to connect the ninth shaft or interconnectingmember 60 with the stationary element or the transmission housing 50 inorder to restrict the member 60 from rotating relative to thetransmission housing 50.

Referring now to FIG. 2 and FIG. 3, the operation of the embodiment ofthe six speed transmission 10 will be described. It will be appreciatedthat transmission 10 is capable of transmitting torque from the inputshaft or member 12 to the output shaft or member 22 in at least sixforward speed or torque ratios and at least one reverse speed or torqueratio. Each forward and reverse speed or torque ratio is attained byengagement of one or more of the torque-transmitting mechanisms (i.e.first clutch 26, second clutch 28, third clutch 30, first brake 32 andsecond brake 34), as will be explained below. FIG. 3 is a truth tablepresenting the various combinations of torque-transmitting mechanismsthat are activated or engaged to achieve the various gear states. An “X”in the box means that the particular clutch or brake is engaged toachieve the desired gear state. An “O” represents that the particulartorque transmitting device (i.e. a brake or clutch) is on or active, butnot carrying torque. A “G” represents that a garage shift element has toswitch on and carrying torque when the transmission mode selector orshifter (Park, Reverse, Neutral, Drive or Low gear selector) is movedfrom reverse to drive and switch off when shifting back to reverse.Actual numerical gear ratios of the various gear states are alsopresented although it should be appreciated that these numerical valuesare exemplary only and that they may be adjusted over significant rangesto accommodate various applications and operational criteria of thetransmission 10. An example of the gear ratios that may be obtainedusing the embodiments of the present invention are also shown in FIG. 3.Of course, other gear ratios are achievable depending on the geardiameter, gear teeth count and gear configuration selected.

To establish a reverse gear, third clutch 30 and second brake 34 areengaged or activated. The third clutch 30 connects the fourth shaft orinterconnecting member 48 with the seventh shaft or interconnectingmember 56. The second brake 34 connects the ninth shaft orinterconnecting member 60 with the stationary element or thetransmission housing 50 in order to restrict the member 60 from rotatingrelative to the transmission housing 50 Likewise, the six forward ratiosare achieved through different combinations of clutch and brakeengagement, as shown in FIG. 3.

It will be appreciated that the foregoing explanation of operation andgear states of the six speed transmission 10 assumes, first of all, thatall the clutches not specifically referenced in a given gear state areinactive or disengaged and, second of all, that during gear shifts,i.e., changes of gear state, between at least adjacent gear states, aclutch engaged or activated in both gear states will remain engaged oractivated.

In another embodiment of the present invention, a transmission 100 isprovided and illustrated in lever diagram form in FIG. 4. Transmission100 includes an input shaft or member 120, a first planetary gear set140, a second planetary gear set 160 and a third planetary gear set 180and an output shaft or member 220. In the lever diagram of FIG. 4, thefirst planetary gear set 140 has three nodes: a first node 140A, asecond node 140B and a third node 140C. The second planetary gear set160 has three nodes: a first node 160A, a second node 160B and a thirdnode 160C. The third planetary gear set 180 has three nodes: a firstnode 180A, a second node 180B and a third node 180C.

The input member 120 is continuously coupled to the first node 180A ofthe third planetary gear set 180. The output member 220 is coupled tothe second node 1408 of the first planetary gear set 140 and the thirdnode 160C the second planetary gear set 160. The third node 140C of thefirst planetary gear set 140 is coupled to a stationary member ortransmission housing 500. The second node 140B of the first planetarygear set 140 is coupled to the third node 160C the second planetary gearset 160. The second node 160B of the second planetary gear set 160 iscoupled to the third node 180C of the third planetary gear set 180.

A first clutch 126 selectively connects the first node 180A of the thirdplanetary gear set 180 and the input member or shaft 120 with the firstnode 160A of the second planetary gear set 160. A second clutch 128selectively connects the first node 180A of the third planetary gear set180 and the input member or shaft 120 with the second node 160B of thesecond planetary gear set 160 and the third node 180C of the thirdplanetary gear set 180. A third clutch 130 selectively connects thefirst node 140A of the first planetary gear set 140 with the second node180B of the third planetary gear set 180. A first brake 132 selectivelyconnects the first node 160A of the second planetary gear set 160 with astationary member or transmission housing 500. A second brake 134selectively connects the second node 1608 of the second planetary gearset 160 with a stationary member or transmission housing 500.

Referring now to FIG. 5, a stick diagram presents a schematic layout ofthe embodiment of the six speed transmission 100 according to thepresent invention. In FIG. 5, the numbering from the lever diagram ofFIG. 4 is carried over. The clutches and couplings are correspondinglypresented whereas the nodes of the planetary gear sets now appear ascomponents of planetary gear sets such as sun gears, ring gears, planetgears and planet gear carriers.

For example, the planetary gear set 140 includes a sun gear member 140C,a ring gear member 140A and a planet gear carrier member 140B thatrotatably supports a set of planet gears 140D (only one of which isshown). The sun gear member 140C is connected to a stationary member ortransmission housing 500 through a first shaft or interconnecting member142. The ring gear member 140A is connected to a second shaft orinterconnecting member 144. The planet carrier member 140B is connectedfor common rotation with a third shaft or interconnecting member 146 andthe output shaft or member 220. The planet gears 140D are eachconfigured to intermesh with both the sun gear member 140C and the ringgear member 140A.

The planetary gear set 160 includes a sun gear member 160A, a ring gearmember 160C and a planet gear carrier member 160B that rotatablysupports a set of planet gears 160D (only one of which is shown). Thesun gear member 160A is connected for common rotation with the fourthshaft or interconnecting member 148 and a fifth shaft or interconnectingmember 152. The ring gear member 160C is connected for common rotationwith the third shaft or interconnecting member 146. The planet carriermember 160B is connected for common rotation with a sixth shaft orinterconnecting member 154 and a seventh shaft or interconnecting member156. The planet gears 160D are each configured to intermesh with boththe sun gear member 160A and the ring gear member 160C.

The planetary gear set 180 includes a sun gear member 180A, a ring gearmember 180C and a planet gear carrier member 180B that rotatablysupports a set of planet gears 180D (only one of which is shown). Thesun gear member 180A is connected for common rotation with the inputshaft or member 120. The ring gear member 180C is connected for commonrotation with the seventh shaft or interconnecting member 156. Theplanet carrier member 180B is connected for common rotation with aneighth shaft or interconnecting member 158. The planet gears 180D areeach configured to intermesh with both the sun gear member 180A and thering gear member 180C.

The input shaft or member 120 is continuously connected to an engine(not shown) or to a turbine of a torque converter (not shown) or inputclutch (not shown). The output shaft or member 220 is continuouslyconnected with the final drive unit or transfer case (not shown).

The torque-transmitting mechanisms or clutches 126, 128, 130 and firstbrake 132 and second brake 134 allow for selective interconnection ofthe shafts or interconnecting members, members of the planetary gearsets and the housing. For example, the first clutch 126 is selectivelyengageable to connect the input shaft or member 120 with the fourthshaft or interconnecting member 148. The second clutch 128 isselectively engageable to connect the input shaft or member 120 with theseventh shaft or interconnecting member 156. The third clutch 130 isselectively engageable to connect the second shaft or interconnectingmember 144 with the eighth shaft or interconnecting member 158. Thefirst brake 132 is selectively engageable to connect the fifth shaft orinterconnecting member 152 with the stationary element or thetransmission housing 500 in order to restrict the member 152 fromrotating relative to the transmission housing 500. The second brake 134is selectively engageable to connect the sixth shaft or interconnectingmember 154 with the stationary element or the transmission housing 500in order to restrict the member 154 from rotating relative to thetransmission housing 500.

Referring now to FIG. 4 and FIG. 5, the operation of the embodiment ofthe six speed transmission 100 will be described. It will be appreciatedthat transmission 100 is capable of transmitting torque from the inputshaft or member 120 to the output shaft or member 220 in at least sixforward speed or torque ratios and at least one reverse speed or torqueratio. Each forward and reverse speed or torque ratio is attained byengagement of one or more of the torque-transmitting mechanisms (i.e.first clutch 126, second clutch 128, third clutch 130, first brake 132and second brake 134), as will be explained below. FIG. 6 is a truthtable presenting the various combinations of torque-transmittingmechanisms that are activated or engaged to achieve the various gearstates. An “X” in the box means that the particular clutch or brake isengaged to achieve the desired gear state. An “O” represents that theparticular torque transmitting device (i.e. a brake or clutch) is on oractive, but not carrying torque. A “G” represents that a garage shiftelement has to switch on and carrying torque when the transmission modeselector or shifter (Park, Reverse, Neutral, Drive or Low gear selector)is moved from reverse to drive and switch off when shifting back toreverse. Actual numerical gear ratios of the various gear states arealso presented although it should be appreciated that these numericalvalues are exemplary only and that they may be adjusted over significantranges to accommodate various applications and operational criteria ofthe transmission 100. An example of the gear ratios that may be obtainedusing the embodiments of the present invention are also shown in FIG. 6.Of course, other gear ratios are achievable depending on the geardiameter, gear teeth count and gear configuration selected.

To establish a reverse gear, first clutch 126 and second brake 134 areengaged or activated. The first clutch 126 connects the input shaft ormember 120 with the fourth shaft or interconnecting member 148. Thesecond brake 134 connects the sixth shaft or interconnecting member 154with the stationary element or the transmission housing 500 in order torestrict the member 154 from rotating relative to the transmissionhousing 500. Likewise, the six forward ratios are achieved throughdifferent combinations of clutch and brake engagement, as shown in FIG.6.

It will be appreciated that the foregoing explanation of operation andgear states of the six speed transmission 100 assumes, first of all,that all the clutches not specifically referenced in a given gear stateare inactive or disengaged and, second of all, that during gear shifts,i.e., changes of gear state, between at least adjacent gear states, aclutch engaged or activated in both gear states will remain engaged oractivated.

The description of the invention is merely exemplary in nature andvariations that do not depart from the gist of the invention areintended to be within the scope of the invention. Such variations arenot to be regarded as a departure from the spirit and scope of theinvention.

The invention claimed is:
 1. A transmission comprising: an input member;an output member; first, second and third planetary gear sets eachhaving first, second and third members; a first interconnecting membercontinuously interconnecting the second member of the first planetarygear set with the third member of the second planetary gear set; asecond interconnecting member continuously interconnecting the thirdmember of the first planetary gear set with a stationary member; a thirdinterconnecting member continuously interconnecting the second member ofthe second planetary gear set with the third member of the thirdplanetary gear set; and five torque transmitting mechanisms eachselectively engageable to interconnect at least one of the first,second, and third members with at least one other of the first, second,third members and the stationary member, and wherein the torquetransmitting mechanisms are selectively engageable in combinations of atleast two to establish at least six forward speed ratios and at leastone reverse speed ratio between the input member and the output member,a first of the five torque transmitting mechanisms is selectivelyengageable to interconnect the first member of the first planetary gearset directly to the second member of the third planetary gear set, and asecond of the five torque transmitting mechanisms is selectivelyengageable to interconnect the first member of the second planetary gearset directly to the second member of the third planetary gear set. 2.The transmission of claim 1 wherein a third of the five torquetransmitting mechanisms is selectively engageable to interconnect thefirst member of the second planetary gear set with the first member ofthe third planetary gear set.
 3. The transmission of claim 2 wherein afourth of the five torque transmitting mechanisms is selectivelyengageable to interconnect the first member of the third planetary gearset with the stationary member.
 4. The transmission of claim 3 wherein afifth of the five torque transmitting mechanisms is selectivelyengageable to interconnect the second member of the third planetary gearset with the stationary member.
 5. The transmission of claim 1 whereinthe input member is continuously connected for common rotation with thefirst member of the second planetary gear set.
 6. The transmission ofclaim 1 wherein the output member is continuously connected for commonrotation with the second member of the second planetary gear set and tothird member of the third planetary gear set.
 7. The transmission ofclaim 1 wherein the input member is continuously connected for commonrotation with the first member of the third planetary gear set.
 8. Thetransmission of claim 1 wherein the output member is continuouslyconnected for common rotation with the second member of the firstplanetary gear set and to third member of the second planetary gear set.9. The transmission of claim 1 wherein the third member of the firstplanetary gear set, the first member of the second planetary gear setand the first member of the third planetary gear set are sun gears, thesecond members of the first, second and third planetary gear sets arecarrier members and the first member of the first planetary gear set,the third member of the second planetary gear set and the third memberof the third planetary gear set are ring gears.
 10. The transmission ofclaim 1 wherein a fourth of the five torque transmitting mechanisms isselectively engageable to interconnect the first member of the secondplanetary gear set with the stationary member.
 11. The transmission ofclaim 10 wherein a fifth of the five torque transmitting mechanisms isselectively engageable to interconnect the second member of the secondplanetary gear set with the stationary member.
 12. A transmissioncomprising: first, second and third planetary gear sets each having asun gear, a carrier member and a ring gear; an input member continuouslyconnected for common rotation with the sun gear of the second planetarygear set; an output member continuously connected for common rotationwith the carrier member of the second planetary gear set and to ringgear of the third planetary gear set; a first interconnecting membercontinuously interconnecting the carrier member of the first planetarygear set with the ring gear of the second planetary gear set; a secondinterconnecting member continuously interconnecting the sun gear of thefirst planetary gear set with a stationary member; a thirdinterconnecting member continuously interconnecting the carrier memberof the second planetary gear set with the ring gear of the thirdplanetary gear set; a first torque transmitting mechanism selectivelyengageable to interconnect the ring gear of the first planetary gear setwith the carrier member of the third planetary gear set; a second torquetransmitting mechanism selectively engageable to interconnect the sungear of the second planetary gear set with the carrier member of thethird planetary gear set; a third torque transmitting mechanismselectively engageable to interconnect the sun gear of the secondplanetary gear set with the sun gear of the third planetary gear set; afourth torque transmitting mechanism selectively engageable tointerconnect the sun gear of the third planetary gear set with thestationary member; and a fifth torque transmitting mechanism selectivelyengageable to interconnect the carrier member of the third planetarygear set with the stationary member, and wherein the torque transmittingmechanisms are selectively engageable in combinations of at least two toestablish at least six forward speed ratios and at least one reversespeed ratio between the input member and the output member.
 13. Atransmission comprising: first, second and third planetary gear setseach having a sun gear, a carrier member and a ring gear; an inputmember continuously connected for common rotation with the sun gear ofthe third planetary gear set; an output member continuously connectedfor common rotation with the carrier member of the first planetary gearset and to ring gear of the second planetary gear set; a firstinterconnecting member continuously interconnecting the carrier memberof the first planetary gear set with the ring gear of the secondplanetary gear set; a second interconnecting member continuouslyinterconnecting the sun gear of the first planetary gear set with astationary member; a third interconnecting member continuouslyinterconnecting the carrier member of the second planetary gear set withthe ring gear of the third planetary gear set; a first torquetransmitting mechanism selectively engageable to interconnect the sungear of the second planetary gear set with the sun gear of the thirdplanetary gear set; a second torque transmitting mechanism selectivelyengageable to interconnect the carrier member of the second planetarygear set with the sun gear of the third planetary gear set; a thirdtorque transmitting mechanism selectively engageable to interconnect thering gear of the first planetary gear set with the carrier member of thethird planetary gear set; a fourth torque transmitting mechanismselectively engageable to interconnect the sun gear of the secondplanetary gear set with the stationary member; and a fifth torquetransmitting mechanism selectively engageable to interconnect thecarrier member of the second planetary gear set with the stationarymember, and wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least two to establish at least sixforward speed ratios and at least one reverse speed ratio between theinput member and the output member.